CN1612981A - Input engaging clutch - Google Patents
Input engaging clutch Download PDFInfo
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- CN1612981A CN1612981A CN02821328.9A CN02821328A CN1612981A CN 1612981 A CN1612981 A CN 1612981A CN 02821328 A CN02821328 A CN 02821328A CN 1612981 A CN1612981 A CN 1612981A
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- spring
- input end
- clutch
- rotation
- described spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
- F16D41/206—Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
A clutch (10) has a rotatable input (12), a rotatable output (16), a spring (18) and a damper mechanism(20, 26). The rotatable input(12)is capable of being rotated and of being held stationary. The spring (18) is coupled to the input (12)such that each time the input (12) changes modes the spring (18) changes states. The damper mechanism (20, 26) allows the spring (18) to change states without rotating the input (12). The rotatable output (16) is positioned relative to the spring (18) such that the output (16) synchronously rotates with the input (12) when the spring (18) is in the first state and rotates independently of the input (12) when the spring (18) is in the second state.
Description
Background of invention
The present invention relates to a kind of input engaging clutch, wherein bring in and make clutch by the input of rotating clutch.When the input end of clutch stopped operating, clutch was thrown off output terminal and input end.
A kind of typical electronic wind spring (wrap spring) clutch comprises input end, output terminal and torque can be sent to the wind spring of output terminal from input end.Usually there is controlling component to link to each other,, thereby engages with wheel hub so that when signal voltage is provided, controllably be wound on spring on the wheel hub and make input end rotation with spring.When removing control signal, controlling component obtains discharging, and spring is unclamped and breaks away from wheel hub.In some applications, to actuate at every turn or all need to actuate or releasing clutch during the input end of releasing clutch.Yet in this structure, clutch all must receive control signal when actuating at every turn or discharging input end, and this signal excitation controlling component is so that clutch and disengagement.Therefore, need a kind of clutch that can under the condition that does not need control signal, make input end and output terminal engage and throw off in some applications.
Brief summary of the invention
The present invention relates to a kind of input engaging clutch.This input engaging clutch has the rotatable input end that can rotate and keep static.This clutch has the wind spring that links to each other with input end.This wind spring has state of equilibrium, and can rotate with input end when input end rotates.Clutch also has the damping mechanism that links to each other with spring, and like this, when input end rotated, damping mechanism can make spring change to deflected-or unclamp or rolling-in from its state of equilibrium.In one embodiment, clutch has rotatable output terminal, and it is located such that with respect to spring output terminal can synchronously rotate with input end when spring is in its deflected, and is independent of the input end rotation when spring is in its state of equilibrium.
Brief description
Fig. 1 is the perspective view according to input engaging clutch of the present invention.
Fig. 2 is the decomposition view of input engaging clutch shown in Figure 1.
Fig. 3 A is the sectional view of input engaging clutch shown in Figure 1.
Fig. 3 B is the end elevation that has shown Fig. 3 A section.
Fig. 4 is the perspective view according to another embodiment of input engaging clutch of the present invention.
Fig. 5 is the decomposition view of input engaging clutch shown in Figure 4.
Fig. 6 A is the sectional view of input engaging clutch shown in Figure 4.
Fig. 6 B is the end elevation that has shown Fig. 6 A section.
Fig. 7 is the perspective view according to another input engaging clutch of the present invention.
Fig. 8 is the sectional view of input engaging clutch shown in Figure 7.
Introduce in detail
Fig. 1 has shown according to input engaging clutch 10 of the present invention.Input engaging clutch 10 comprises input end 12, shell 14 and output terminal 16.In operation, input engaging clutch 10 can make input end 12 and output terminal 16 alternately engage or throw off.For example, input end 12 has two kinds of patterns: it can be along the rotation of direction, does not perhaps rotate and keeps static.Input end 12 can link to each other with motor, can be switched on or switched off motor and come rotating force alternately to be provided and rotating force is not provided for input end 12.Output terminal 16 can link to each other with the device such as the gear that door is moved.When the motor that links to each other with input end 12 was shut down, input engaging clutch 10 was thrown off, and makes input end 12 and output terminal 16 no longer link together.Input end 12 remains static when motor is shut down.Yet when motor was connected, input end 12 changed to rotary mode.When motor was connected, input end 12 was forced to rotation, made input engaging clutch 10 engage, and input end 12 is linked to each other with output terminal 16, made output terminal 16 with input end 12 rotations.
Fig. 2 has shown the decomposition view according to input engaging clutch 10 of the present invention.Input engaging clutch 10 comprises input end 12, shell 14, positioning ring 15, output terminal 16, output shaft 17, wind spring 18, spring spool 20, output hub 22 and end cap 24.Output hub 22 and end cap 24 are press-fit on the output shaft 17, thereby form one with output shaft 17.When clutch 10 was fully assembled, positioning ring 15 helped assembly is kept together.
Wind spring 18 is springs of a kind of coiled coil, and it has the relaxed state that defines lax internal diameter.Input end 12 comprises input wheel hub 13, and it has the wheel hub external diameter.Be in the external diameter of the internal diameter of the wind spring 18 under its relaxed state less than input wheel hub 13.Therefore, in the time of on wind spring 18 being placed input wheel hub 13, they are in interference fit.Therefore, wind spring 18 rotates with input end 12 when input end 12 rotations.Wind spring 18 also can comprise the first pogo pin 19A, and it can engage with input end 12, so that guarantee that further wind spring 18 also can rotate because of their joint when 12 rotations of input wheel hub.
When input engaging clutch 10 is fully assembled and input end 12 when not rotating, wind spring 18 is in state of equilibrium.Wind spring 18 has the second pogo pin 19B, and it is configured to can be assembled in the groove 21 of spring spool 20.Because input end 12, wind spring 18, the second pogo pin 19B and spring spool 20 interconnect, so spring spool 20 is configured to and can rotates with input end 12 when input end 12 rotations.Yet when wind spring 18 was in its state of equilibrium, output shaft 17 and input end 12 were thrown off.Under its state of equilibrium, the internal diameter of wind spring 18 is greater than the external diameter of output hub 22.Therefore, when wind spring 18 is in its state of equilibrium following time, output shaft 17 can rotation freely in wind spring 18, can not form interference with it.
Wind spring 18 can unclamp from its state of equilibrium or rolling-in and enter into deflected.When spring 18 rolling-in, the internal diameter when its internal diameter will be less than its balance.When spring 18 unclamps, the internal diameter when its internal diameter will be greater than its balance.Input engaging clutch 10 has utilized wind spring 18 from the advantage that its state of equilibrium changes to its deflected input end 12 to be engaged with output terminal 16.For example, can be to output hub 22 with wind spring 18 rolling-in, make the rotation of input end 12 will cause the rotation of output shaft 17.
Fig. 3 has shown the sectional view of the input engaging clutch 10 that is fully assembled.Input engaging clutch 10 comprises input end 12, input wheel hub 13, shell 14, output terminal 16, output shaft 17, wind spring 18, output hub 22, end cap 24 and viscous fluid 26.In operation, in response to the alternate of input end 12 between rotary mode and still-mode, input engaging clutch 10 can be used to make input end 12 and output terminal 16 alternately to engage and throws off.
When input engaging clutch 10 was fully assembled, viscous fluid 26 was contained in the zone between shell 14 and the spring spool 20, thereby has surrounded spring spool 20.When input end 12 was in rotary mode, input end 12 can make wind spring 18 and spring spool 20 rotate because of it interconnects.The external diameter of the 26 pairs of spring spools 20 of viscous fluid in the zone between spring spool 20 and shell 14 provides the resisting moment opposite with its rotation.The resisting moment that acts on by viscous fluid 26 provided on the spring spool 20 can change along with the viscosity of the speed of input end 12 rotations and viscous fluid 26.In some cases, for example under the very low situation of the rotational speed of input end 12 viscosity very low and viscous fluid 26, act on resisting moment on the external diameter of spring spool 20 may deficiency so that wind spring 18 rolling-in on output hub 22.Yet, under enough rotational speeies and viscosity, thisly be enough to cause wind spring 18 to be converted to its deflected from its state of equilibrium by the resisting moment on the caused external diameter that acts on spring spool 20 of viscous fluid 26.Specifically, the resisting moment that acts on the external diameter of spring spool 20 will cause wind spring 18 rolling-in on input wheel hub 13 and output hub 22, thereby clutch 10 is engaged.
When input end 12 from rotary mode be converted to still-mode and thereby when stopping the rotation, can dissipate by viscous fluid 26 caused resisting moment.Simultaneously, rolling-in has stored energy to wind spring 18 under the deflected on input wheel hub 13 and the output hub 22 rotating with input end 12.When input end 12 stopped the rotation, the energy that is stored in the wind spring 18 can cause wind spring 18 to unclamp.This energy that is stored in the wind spring 18 dissipates by the rotation of spring spool 20 in fluid 26.Therefore, when input end 12 when its rotary mode is converted to its still-mode, wind spring 18 will change back to its state of equilibrium from its deflected.This a small amount of rotation of wind spring 18 and spring spool 20 make output hub 22 from state that wind spring 18 engages discharge, thereby clutch 10 is thrown off.
Like this, when under the speed that is being higher than threshold velocity input end 12 being applied the input end rotatory force, clutch 10 will engage, and promptly input end 12 is with output shaft 17 rotations.When input end 12 stops operating, input engaging clutch 10 will be thrown off, and promptly output hub 22 and output shaft 17 can be independent of input end 12 and rotate.Under this disengaged condition, output shaft 17 can rotation freely in wind spring 18.The disengagement of clutch 10 does not rely on the counterrotating of input end 12.
Input engaging clutch 10 can be used in the application that needs the clutch that engages and throw off when applying rotating force in input end when rotation stops.For example, in some applications, the gear mechanism by some type can be applied to rotatory force on the input end 12 of input engaging clutch 10.Input end 12 also will rotate when this gear mechanism rotation, cause wind spring 18 rolling-in on input wheel hub 13 and output hub 22, make output shaft 17 with input end 12 rotations.In some structures, when the active force of this gear-type that offers input end 12 stopped the rotation, input end 12 was stopped on the direction opposite with its original driving direction and rotates.Like this, the energy that is stored in the wind spring 18 can not dissipate by making input end 12 counterrotatings and unclamping wind spring 18.On the contrary, input engaging clutch 10 allows by rotating spring sleeve 20 wind spring 18 to be unclamped.When making sleeve 20 motion that wind spring 18 is unclamped, output shaft 17 obtains discharging, and input engaging clutch 10 is thrown off.Be enough to overcome resisting moment on the external diameter that acts on spring spool 20 that viscous fluid 26 provided as long as be stored in energy in the wind spring 18, wind spring 18 just can unclamp and discharge output shaft 17.
Clutch 10 can be used for automatically and manually mobile car door.Can actuate the drive motor that links to each other with input end 12 and drive the gear that links to each other with output terminal 16, output terminal 16 drives car door and automatically moves.When drive motor was shut down, clutch 10 was thrown off, thereby allows manually mobile car door, need not operate the drive motor that links to each other with input end 12.
Clutch 10 also can be used as the amplification damper.For example, clutch 10 can be configured to the housing damper, it provides with respect to base or the closed constant speed of substrate (ground) for housing.Like this, input end 12 with treat that closed housing links to each other, 16 of shell 14 and output terminals link to each other with substrate.Because housing trends towards relative substrate closure because of acting on its qualitative gravity, so input end 12 will rotate.Because on output terminal 16, so the closing speed of 10 pairs of housings of clutch provides restriction to spring 18 with rolling-in for the more high rotation speed of input end 12.The spring spool 20 of rotation provides resistance for the closure of housing in viscous fluid 26, thereby provides required closure feature for housing.
Fig. 4-6 has shown according to another input engaging clutch 40 of the present invention.Clutch 40 comprises input end 42, input wheel hub 43, positioning ring 44, hold-down ring 45, output terminal 46, output shaft 47, wind spring 48, resistance spring 50, output hub 52, gear 54, gear hub 56, damping gear 58 and rotation damper 59.In operation, alternately rotate and keep static in response to input end 42, input engaging clutch 10 can be used to make input end 42 and output terminal 46 alternately to engage and throws off.
Similar with above-mentioned wind spring 18 and input engaging clutch 10, wind spring 48 links to each other with input end 42 by input wheel hub 43.Wind spring 48 has certain lax internal diameter when being in relaxed state.The internal diameter of wind spring 48 under its relaxed state is less than the diameter of input wheel hub 43.Like this, when clutch 40 was fully assembled, wind spring 48 engaged with input end 42 friction types, specifically engaged with input wheel hub 43.As an alternative or additional, wind spring 48 can comprise the first pogo pin 49A, and it can engage with input end 42, thereby wind spring 48 is further linked to each other with input end 42.Like this, wind spring 48 rotates with the rotation of input end 42.
In operation, clutch 40 makes input end 42 alternately engage with output terminal 46 or throws off.When clutch 40 is fully assembled and input end 42 when not rotating, wind spring 48 is in state of equilibrium.When input end 42 was in rotary mode, input end 42 rotation was got up, and wind spring 48 also since between them interconnect and with input end 42 rotations.When input end 42 along direction 60 (shown in Fig. 4) when turning clockwise, wind spring 48 is also along 60 rotations of identical direction.When input end 42 during along direction 60 rotation, the second pogo pin 49B engages with the resistance spring pin 53 of resistance spring 50.This will make resistance spring 50 along the direction rotation identical with input end 42 and wind spring 48.Gear 54 trends towards along the direction identical with input end 42 60 rotations because of the interference fit between resistance spring 50 and the gear hub 56.Because tooth on the gear 54 and the interconnection of the tooth on the damping gear 58, so damping gear 58 trends towards along the counter clockwise direction rotation opposite with direction 60.Damping gear 58 links to each other with rotation damper 59, and rotation damper 59 is configured to provide resisting moment, makes damping gear 58 provide resistance for the rotation of gear 54.For the low-down rotating speed of input end 42 and the enough low resisting moment that is provided by damping gear 58 and rotation damper 59, the second pogo pin 49B of wind spring 48 can make resistance spring 50 rotations by resistance spring pin 53, and it is enough to prevent that wind spring 48 rolling-in are on output hub 52.Yet, having very big rotating speed and damping gear 58 and rotation damper 59 at input end 42 is configured to provide under the situation of very big resisting moment, the second pogo pin 49B of wind spring 48 can't make resistance spring 50 and gear 54 rotate with sufficiently high rotating speed, thereby can't prevent that wind spring 48 rolling-in are on input wheel hub 43 and output hub 52.Like this, wind spring 48 will be converted to its deflected from its state of equilibrium.When wind spring 48 rolling-in were on input wheel hub 43 and output hub 52, clutch 40 engaged, and output shaft 47 will rotate with the rotation of input end 42.When input end 42 when its rotary mode is converted to its still-mode, the energy that is stored on output hub 52 in the wind spring 48 because of rolling-in trends towards dissipating.The energy of being stored will unclamp from its deflected by wind spring 48 to be got back to its state of equilibrium and dissipates.In many cases, because input end 42 has been prevented from along the direction rotation opposite with original sense of rotation 60, so when wind spring 48 unclamps, the second pogo pin 49B will rotate against resistance spring pin 53, and therefore making resistance spring 50, gear 54 and gear hub 56 along direction 60 rotations, this direction is and the identical direction of input end 42 initial rotations.Then because tooth on the gear 54 and the tooth on the damping gear 58 interconnection, damping gear 58 will be along the direction rotation opposite with direction 60.When wind spring 48 unclamped its state of equilibrium from its deflected, clutch 40 was thrown off.That is to say that when wind spring 48 was in its state of equilibrium, output shaft 47 can and not rely on input end 42 in wind spring 48 and freely rotates.
Though for the present invention not necessarily, this slip of resistance spring 50 in clutch 40 is favourable in some applications.For example, rotation damper 59 may be merely able to correctly work in the certain speed range that comprises some acceptable maximum (top) speeds of swing pinion 58.In some cases, input end 42 can rotate under the much higher rotational speed that can bear than rotation gear 58.Can't come under the situation of governing speed difference by adjusting gear ratio, this slip of resistance spring 50 in clutch 40 can provide good solution.
The amount that wind spring 48 must rotate before on the output hub 46 in its rolling-in is defined as the rolling-in angle.This rolling-in angle is big more, just has many more energy will be stored in the spring 48.The energy that is stored in when spring 48 is in deflected in the spring 48 is enough to overcome the resisting moment of coming self-damping gear 58 and rotation damper 59, make spring 48 change and to make gear 54 and 58 rotations of damping gear, thereby clutch 40 is thrown off from its deflected to its state of equilibrium.For damping gear 58 and rotation damper 59, many kinds of rotation dampers all are to accept.The example of the acceptable ready-made rotation damper of the present invention is the product of FRT-C2, FRN-C2, FRT-D2 and FRN-D2 for the model from Ace ControlsInternational company.The damper of these types includes viscous fluid, and it can make damper have rotational resistance with velocity correlation.Those skilled in the art will appreciate that to provide many kind structures of rotational resistance all can be used as damper in the present invention.
Also can revise input engaging clutch 40, make it can be used as the input engaging clutch that joint is then thrown off when input end 42 is in its still-mode when input end 42 is converted to its rotary mode according to the present invention.This result opposite with above-mentioned clutch 40 can and make gear 54 and rotation damper 58 realize with respect to input end 43 motions on input wheel hub 43 and output hub 52 by making wind spring 48 rolling-in when its state of equilibrium.When input end 43 when its still-mode is converted to its rotary mode, wind spring 48 unclamps and enters its deflected from output hub 52.Under this deflected, output hub 52 can freely rotate in wind spring 48, and this clutch of revising 40 is thrown off.When input end 43 when its rotary mode is converted to its still-mode, wind spring 48 rolling-in are on output hub 52 and get back to its state of equilibrium.Under this state of equilibrium, output hub 52 links to each other with wind spring 48, and this clutch of revising 40 engages.
The input engaging clutch 40 of this modification can be used in many application.For example, it can combine use with the braking system that is used for wheeled vehicle.Input end 42 can with alternately rotate with keeping static with the motion of vehicle and keep static wheel to link to each other.And output shaft 47 can be fixed in vehicle or the substrate, makes it non-rotatable.When the wheel that links to each other with input end 42 did not rotate, input end 42 was in still-mode and does not rotate.Under this pattern, this input engaging clutch of revising 40 engages, and makes input end 42 and output terminal 46 link together.Because output shaft 47 is fixed and can not rotates, therefore when input end 42 was in this still-mode, the clutch 40 of this modification can be used as break.Yet when wheel rotated, input end 42 was converted to rotary mode.Input end 42 is forced to rotate with wheel, causes the input engaging clutch 40 of this modification to be thrown off, and just input end 42 no longer links to each other with output shaft 47, thereby output shaft 47 no longer is connected on the input end 42.When input end 42 was in the rotary mode, the braking effect that this release of input end 42 from output shaft 47 can cause existing when input end 42 is in still-mode obtained discharging.
The input engaging clutch 40 of this modification also can be used under the overload situation.For example, traditional electrical spring formula clutch can use under normal operation, and the clutch of revising 40 can form joint being in connection under the overload situation, make the rotation of input end 42 and the output terminal 46 of clutch 40 of this modification break away from, and the clutch revised 42 is discharged from substrate.
Fig. 7 and 8 has shown according to another two-way input engaging clutch 200 of the present invention.Clutch 200 comprises input end 242, input wheel hub 243, positioning ring 244, hold-down ring 245, output terminal 246, wind spring 248, resistance spring 250, external gear 254, internal gear 255, small gear 257, damping gear 258, rotation damper 259, input end housing 260 and shell 261.Output terminal 246 comprises output shaft 247, inner wheel hub 252 and outer wheel hub 253, and all these parts all are whole, thereby can rotate together.
Input engaging clutch 200 operate similarly with input engaging clutch 40, and the part that makes an exception is that input engaging clutch 200 can operate by bidirectional mode.Specifically, input end 242 can link to each other with driving force, and this driving force alternately makes input end 242 along rotating clockwise and counterclockwise.Output terminal 246 can be connected to such as on the device of gear that can open and close door.When cutting off with driving force that input end 242 links to each other, input end 242 is in still-mode and does not rotate.Under this pattern, input engaging clutch 200 is thrown off, and makes input end 242 and output terminal 246 no longer link together.Yet when driving force was provided, input end 242 was converted to rotary mode.When input end 242 is forced to when rotating clockwise or counterclockwise, input engaging clutch 240 will engage, and input end 242 is linked to each other with output terminal 246, make output shaft 247 with input end 242 rotations.
Wind spring 248 links to each other with input end 242, so the rotation of input end 242 also can make wind spring 248 rotations.Input end 242 has the circular trough that is cut in the input wheel hub 243, wind spring 248 can be press-fit to like this in the groove on the input wheel hub 243.Wind spring 248 is press-fit to can guarantees in the input end 242 that wind spring 248 rotates constantly with input end 242, and with the irrelevant to rotation direction of input end 242.Wind spring 248 can link to each other with input end 242 in every way, introduced a kind of method wherein in the U.S. Patent No. 4638899 (Kossett) that is entitled as " clutch spring being fixed on method for simplifying and related device on the torque input wheel hub of spring clutch ", this patent is incorporated herein by reference.
With introduced at input engaging clutch 40 similar, the wind spring 248 of input engaging clutch 200 comprises and is configured to the pogo pin (not shown among Fig. 8) that engages with resistance spring 250.The internal diameter of resistance spring 250 under its relaxed state is less than the external diameter of internal gear 255.Like this, when being fully assembled clutch 200, resistance spring 250 engages with internal gear 255 friction types.Internal gear 255 is configured to and can engages with small gear 257 when internal gear 255 rotations.In a preferred embodiment, internal gear 255 and small gear 257 all have the tooth that can mesh when rotated.Small gear 257 is configured to and external gear 254 engagements.External gear 254 have similarly be configured to can with the tooth of tooth on the small gear 257 engagement.At last, damping gear 258 also have be configured to can with the tooth of external gear 254 engagement.When being fully assembled clutch 200, positioning ring 244 and hold-down ring 245 help assembly is kept together.Housing 260 surrounds and has protected a part of clutch 200, and links to each other so that they can be with output terminal 246 rotations with outer wheel hub 253.Shell 261 surrounds and has protected external gear 254 and rotation damper 259.
In operation, clutch 200 alternately makes input end 242 and output terminal 246 engage and throws off.When input end 242 rotated clockwise or counterclockwise, it was in rotary mode.Under this rotary mode, because wind spring 248 and input end 242 interconnection, wind spring 248 also will rotate with input end 242.Because the respective springs pin (not shown among Fig. 8) of resistance spring 250 and wind spring 248 engages, so the rotation of wind spring 248 also will make resistance spring 250 rotations.This joint of not shown pogo pin in Fig. 8, but its basically with Fig. 4 in by pogo pin 49B, 51 is shown with 53 and described identical in conjunction with above-mentioned clutch 40.Like this, rotation wind spring 248 can make resistance spring 250 rotations, and this makes internal gear 255 rotations again, internal gear 255 makes small gear 257 rotations, this makes external gear 254 rotation again, and external gear 254 makes 258 rotations of damping gear again, and all these are all because of due to the interconnection of the respective teeth on these gears.Damping gear 258 links to each other with rotation damper 259, and this damper structure becomes metastable resisting moment can be provided, and makes damping gear 258 that metastable rotational resistance is provided.When input end 242 rotated with enough rotating speeds along clockwise direction, rotation damper 259 caused wind spring 248 rolling-in to inner wheel hub 252 by damping gear 258, external gear 254, small gear 257, internal gear 255 and resistance spring 250.When wind spring 248 rolling-in were to inner wheel hub 252, clutch 200 engaged, and just output terminal 256 and output shaft 247 will be with input end 242 rotations.Similarly, when input end 242 rotates with enough rotating speeds in the counterclockwise direction, rotation damper 259 provides enough resisting moment, and causes wind spring 248 to unclamp on the outer wheel hub 253 by damping gear 258, external gear 254, small gear 257, internal gear 255 and resistance spring 250.Like this, being rotated counterclockwise of input end 242 engages clutch 200, and just output terminal 246 and output shaft 247 will be with input end 242 rotations.
When input end 242 from its rotary mode (clockwise or be rotated counterclockwise) when being converted to its still-mode, produce the energy that deflection is stored in the wind spring 248 on the outer wheel hub 253 and will dissipate on inner wheel hub 252 or by rolling-in by unclamping.This stored energy will be unclamped or rolling-in to its state of equilibrium dissipates from its deflected by wind spring 248.In many cases, because input end 242 has been prevented from along the direction rotation opposite with initial sense of rotation, therefore unclamp or during rolling-in when wind spring 248, the pogo pin of wind spring 248 will engage with the pogo pin on the resistance spring 250, thereby makes resistance spring 250, internal gear 255, small gear 257, external gear 254 and 258 rotations of damping gear.This rotation can make wind spring 248 get back to its state of equilibrium, thereby clutch 200 is thrown off, and just output terminal 246 is independent of input end 242 and rotates.
Though introduced the present invention hereinbefore, yet it will be understood by those of skill in the art that under the premise without departing from the spirit and scope of the present invention, can make amendment to the present invention in form and details with reference to preferred embodiment.
Claims (20)
1. clutch comprises:
Rotatable input end;
Spring with state of equilibrium and deflected, described spring links to each other with described input end, makes described spring to rotate with described input end when described input end rotates;
The damping mechanism that links to each other with described spring, described damping mechanism can be transformed into rotation and the time make described spring be converted to its deflected from its state of equilibrium from static at described input end, and described damping mechanism is transformed into from rotation at described input end and allows described spring to be converted to its state of equilibrium from its deflected when static; With
The rotatable output terminal of locating with respect to described spring, when described spring is in its deflected, described output terminal can synchronously rotate with described input end, and when described spring was in its state of equilibrium, described output terminal can be independent of described input end and rotate.
2. clutch according to claim 1 is characterized in that, described rotatable output terminal comprises the output hub that is positioned at described spring, like this, when described input end changes to when rotation from static, but described spring rolling-in on described output hub, thereby make described clutch.
3. clutch according to claim 2 is characterized in that, the described output hub in the described spring be configured to when described input end from rotation change when static, described spring can unclamp from described output hub, thereby makes described throw-out-of clutch.
4. clutch according to claim 3 is characterized in that, described spring is by rotating described damping mechanism but do not rotate described input and bring in from described output hub and unclamp.
5. clutch according to claim 4 is characterized in that described damping mechanism comprises spring spool, and it links to each other with described spring and is surrounded by viscous fluid.
6. clutch according to claim 4 is characterized in that described damping mechanism comprises rotation damper, and it links to each other with described spring by at least one gear.
7. clutch according to claim 6 is characterized in that described rotation damper provides rotational resistance.
8. clutch according to claim 1 is characterized in that, described rotatable output terminal comprises the output hub that has surrounded described spring, like this, when described input end changes to when rotation from static, described spring unclamps on the described output hub, thereby makes described clutch.
9. clutch according to claim 8 is characterized in that, the described output hub that has surrounded described spring be configured to when described input end from rotation change when static, described spring rolling-in also breaks away from described output hub, thereby makes described throw-out-of clutch.
10. clutch comprises:
Rotatable input end with first pattern and second pattern;
Spring with first state and second state, described spring links to each other with described input end, makes that described spring can change state when each described input end changed pattern;
With the damping device that described spring links to each other, it allows to make under the situation of not rotating described input end described spring to change state; With
The rotatable output terminal of locating with respect to described spring, when described spring is in described first state, described output terminal can synchronously rotate with described input end, and when described spring was in described second state, described output terminal can be independent of described input end and rotate.
11. clutch according to claim 10 is characterized in that, described input end is static in described first pattern, and in described second pattern along clockwise or be rotated counterclockwise.
12. clutch according to claim 11 is characterized in that, described rotatable output terminal comprises the output hub that is positioned at described spring, like this, when described input end changes to when rotation from static, but described spring rolling-in to described output hub, thereby make described clutch.
13. clutch according to claim 11 is characterized in that, the described output hub in the described spring be configured to when described input end from rotation change when static, described spring can unclamp from described output hub, thereby makes described throw-out-of clutch.
14. clutch according to claim 13 is characterized in that, described spring is by rotating described damping device but do not rotate described input and bring in from described output hub and unclamp.
15. clutch according to claim 14 is characterized in that, described damping device comprises the spring spool that is surrounded by viscous fluid, and described spring spool links to each other with described spring.
16. clutch according to claim 10, it is characterized in that, described input end is static under described first pattern, and under described second pattern, rotate, described rotatable output terminal comprises the output hub that is positioned at described spring, like this, and when described input end changes to when rotation from static, described spring can unclamp from described output hub, thereby makes described throw-out-of clutch.
17. clutch according to claim 16 is characterized in that, the described output hub in the described spring be configured to when described input end from rotation change when static, but described spring rolling-in to described output hub, thereby make described clutch.
18. a clutch comprises:
Rotatable input end with first pattern and second pattern;
Spring with state of equilibrium and deflected, described spring links to each other with described input end, makes that described spring can change state when each described input end changed pattern;
With the rotation damper that described spring links to each other, described damper allows to make under the situation of not rotating described input end described spring to change state; With
The rotatable output terminal of locating with respect to described spring, when described spring is in described first state, described output terminal can synchronously rotate with described input end, and when described spring was in described second state, described output terminal can be independent of described input end and rotate.
19. clutch according to claim 18 is characterized in that, described rotation damper links to each other with described spring by at least one gear.
20. clutch according to claim 19 is characterized in that, resistance spring provides slip between described rotation damper and described spring.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US31649301P | 2001-08-31 | 2001-08-31 | |
| US60/316,493 | 2001-08-31 | ||
| US10/092,165 | 2002-03-05 | ||
| US10/092,165 US6637571B2 (en) | 2001-08-31 | 2002-03-05 | Input engaging clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1612981A true CN1612981A (en) | 2005-05-04 |
Family
ID=26785353
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN02821328.9A Pending CN1612981A (en) | 2001-08-31 | 2002-08-28 | Input engaging clutch |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US6637571B2 (en) |
| EP (1) | EP1432923A4 (en) |
| CN (1) | CN1612981A (en) |
| AU (1) | AU2002332700A1 (en) |
| WO (1) | WO2003021124A2 (en) |
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| CN101943226A (en) * | 2009-07-02 | 2011-01-12 | 拓基轴承株式会社 | Inverted input blocking mechanism |
| CN102563055A (en) * | 2010-12-23 | 2012-07-11 | 通用汽车环球科技运作有限责任公司 | Transmission with selectable one-way clutch and dual-piston clutch |
| CN105697573A (en) * | 2014-12-15 | 2016-06-22 | 舍弗勒技术股份两合公司 | Assembly with friction device |
| CN106483438A (en) * | 2015-08-28 | 2017-03-08 | 神讯电脑(昆山)有限公司 | Crystal tube detection device |
| CN108006104A (en) * | 2018-01-03 | 2018-05-08 | 成都云鼎康德科技有限公司 | A kind of Pneumatic unidirectional clutch |
| CN109070203A (en) * | 2016-03-30 | 2018-12-21 | 东洋机械金属株式会社 | Electric press casting machine |
| CN109854642A (en) * | 2019-03-19 | 2019-06-07 | 上海杰邦塑料五金制品有限公司 | A kind of clutch gear damper |
| CN113982409A (en) * | 2020-07-27 | 2022-01-28 | 麦格纳覆盖件有限公司 | Power actuator unit with mechanically actuated clutch/brake assembly |
| CN115038885A (en) * | 2020-01-31 | 2022-09-09 | 里尔精密制造公司 | Damper control type coiled spring clutch |
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| US7080719B2 (en) * | 2004-09-07 | 2006-07-25 | Reell Precision Manufacturing Corporation | Wrap spring brake |
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| DE102005046384B4 (en) * | 2005-09-28 | 2014-08-07 | Em Kunststofftechnik Gmbh | Slip clutch for an electromotive adjusting device |
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| US2106744A (en) * | 1934-03-19 | 1938-02-01 | Corning Glass Works | Treated borosilicate glass |
| US3394785A (en) * | 1966-04-26 | 1968-07-30 | Ibm | Latch operated energy trap power transmission |
| US3938974A (en) * | 1973-04-27 | 1976-02-17 | Macedo Pedro B | Method of producing optical wave guide fibers |
| IT1033333B (en) | 1974-04-24 | 1979-07-10 | Nixdorf Computer Ag | JOINT WITH CYLINDRICAL HELICAL SPRING |
| CA1126672A (en) | 1976-12-13 | 1982-06-29 | Robert L. Wahlstedt | Electro magnetic spring clutch |
| US4433765A (en) | 1982-09-13 | 1984-02-28 | General Clutch Corp. | Spring clutches |
| JPS59123732U (en) * | 1983-02-09 | 1984-08-20 | 不二精器株式会社 | Rotating damper with directionality |
| JPS63171736U (en) * | 1987-04-30 | 1988-11-08 | ||
| US5250095A (en) * | 1988-08-16 | 1993-10-05 | Rutgers University | Method for making porous glass optical fiber sensor |
| JPH0678703B2 (en) * | 1989-05-02 | 1994-10-05 | スガツネ工業株式会社 | Damper for flap door using viscous fluid |
| JP2649734B2 (en) | 1989-10-11 | 1997-09-03 | 三田工業株式会社 | Electromagnetic control spring clutch mechanism |
| US5133437A (en) | 1991-01-28 | 1992-07-28 | Reell Precision Manufacturing | Wrap spring clutch with brake |
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| US5170867A (en) * | 1991-07-23 | 1992-12-15 | Nhk Spring Co., Ltd. | Pedal parking brake |
| ES2089405T3 (en) * | 1992-07-08 | 1996-10-01 | Sugatsune Kogyo | SHOCK ABSORBER DEVICE FOR AUTOMATIC FOLDING ARMCHAIR. |
| US5464083A (en) | 1993-08-31 | 1995-11-07 | Reell Precision Manufacturing Corporation | Torque limiting spring hinge |
| JP3304188B2 (en) * | 1994-02-23 | 2002-07-22 | 株式会社ニフコ | One-way rotary damper |
| US5585640A (en) * | 1995-01-11 | 1996-12-17 | Huston; Alan L. | Glass matrix doped with activated luminescent nanocrystalline particles |
| US5697125A (en) | 1995-11-27 | 1997-12-16 | Reell Precision Manufacturing Corporation | Clip friction hinge |
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| EP0970396B1 (en) * | 1997-03-29 | 2004-09-22 | Deutsche Telekom AG | Fiber-integrated photon crystals and systems |
| US5950783A (en) * | 1998-08-04 | 1999-09-14 | Lexmark International, Inc. | Self adjusting wrap spring clutch |
-
2002
- 2002-03-05 US US10/092,165 patent/US6637571B2/en not_active Expired - Lifetime
- 2002-08-28 EP EP02797769A patent/EP1432923A4/en not_active Withdrawn
- 2002-08-28 WO PCT/US2002/027399 patent/WO2003021124A2/en not_active Application Discontinuation
- 2002-08-28 AU AU2002332700A patent/AU2002332700A1/en not_active Abandoned
- 2002-08-28 CN CN02821328.9A patent/CN1612981A/en active Pending
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101943226B (en) * | 2009-07-02 | 2014-10-15 | 拓基轴承株式会社 | Inverted input blocking mechanism |
| CN101943226A (en) * | 2009-07-02 | 2011-01-12 | 拓基轴承株式会社 | Inverted input blocking mechanism |
| CN102563055A (en) * | 2010-12-23 | 2012-07-11 | 通用汽车环球科技运作有限责任公司 | Transmission with selectable one-way clutch and dual-piston clutch |
| CN102563055B (en) * | 2010-12-23 | 2014-10-08 | 通用汽车环球科技运作有限责任公司 | Transmission with selectable one-way clutch and dual-piston clutch |
| CN105697573B (en) * | 2014-12-15 | 2022-03-29 | 舍弗勒技术股份两合公司 | Assembly with friction device |
| CN105697573A (en) * | 2014-12-15 | 2016-06-22 | 舍弗勒技术股份两合公司 | Assembly with friction device |
| CN106483438A (en) * | 2015-08-28 | 2017-03-08 | 神讯电脑(昆山)有限公司 | Crystal tube detection device |
| CN106483438B (en) * | 2015-08-28 | 2018-08-28 | 神讯电脑(昆山)有限公司 | Crystal tube detection device |
| CN109070203A (en) * | 2016-03-30 | 2018-12-21 | 东洋机械金属株式会社 | Electric press casting machine |
| CN108006104A (en) * | 2018-01-03 | 2018-05-08 | 成都云鼎康德科技有限公司 | A kind of Pneumatic unidirectional clutch |
| CN109854642A (en) * | 2019-03-19 | 2019-06-07 | 上海杰邦塑料五金制品有限公司 | A kind of clutch gear damper |
| CN115038885A (en) * | 2020-01-31 | 2022-09-09 | 里尔精密制造公司 | Damper control type coiled spring clutch |
| US12031587B2 (en) | 2020-01-31 | 2024-07-09 | Reell Precision Manufacturing Corporation | Damper controlled wrap spring clutch |
| CN115038885B (en) * | 2020-01-31 | 2024-08-30 | 里尔精密制造公司 | Coiled spring clutch and bidirectional coiled spring clutch |
| CN113982409A (en) * | 2020-07-27 | 2022-01-28 | 麦格纳覆盖件有限公司 | Power actuator unit with mechanically actuated clutch/brake assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2003021124A2 (en) | 2003-03-13 |
| US20030042099A1 (en) | 2003-03-06 |
| WO2003021124A3 (en) | 2003-11-13 |
| EP1432923A4 (en) | 2006-07-05 |
| EP1432923A2 (en) | 2004-06-30 |
| AU2002332700A1 (en) | 2003-03-18 |
| US6637571B2 (en) | 2003-10-28 |
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Legal Events
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| C06 | Publication | ||
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| C10 | Entry into substantive examination | ||
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| AD01 | Patent right deemed abandoned | ||
| C20 | Patent right or utility model deemed to be abandoned or is abandoned |